WO2016061079A1 - Hydraulic actuator lockout - Google Patents

Hydraulic actuator lockout Download PDF

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Publication number
WO2016061079A1
WO2016061079A1 PCT/US2015/055294 US2015055294W WO2016061079A1 WO 2016061079 A1 WO2016061079 A1 WO 2016061079A1 US 2015055294 W US2015055294 W US 2015055294W WO 2016061079 A1 WO2016061079 A1 WO 2016061079A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
piston
configuration
lockout assembly
chamber
Prior art date
Application number
PCT/US2015/055294
Other languages
English (en)
French (fr)
Inventor
Brian Hoemke
Shawn Justin POLLOCK
Adam J. Kurzynski
Aaron Hrdlichka
Original Assignee
Woodward, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Woodward, Inc. filed Critical Woodward, Inc.
Priority to CN201580067731.0A priority Critical patent/CN107002718B/zh
Priority to EP15790724.7A priority patent/EP3207262A1/de
Publication of WO2016061079A1 publication Critical patent/WO2016061079A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K35/00—Means to prevent accidental or unauthorised actuation
    • F16K35/10—Means to prevent accidental or unauthorised actuation with locking caps or locking bars
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0438—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being of the nozzle-flapper type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/04—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor
    • F16K31/423—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor the actuated members consisting of multiple way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K35/00—Means to prevent accidental or unauthorised actuation
    • F16K35/02—Means to prevent accidental or unauthorised actuation to be locked or disconnected by means of a pushing or pulling action
    • F16K35/022—Means to prevent accidental or unauthorised actuation to be locked or disconnected by means of a pushing or pulling action the locking mechanism being actuated by a separate actuating element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K35/00—Means to prevent accidental or unauthorised actuation
    • F16K35/16—Means to prevent accidental or unauthorised actuation with locking member actuated by magnet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]

Definitions

  • This instant specification relates to lockout devices for fluid actuators controlled by fluid servo valves and solenoid valves.
  • Servo valves and solenoids can be used to control fluid flow, for example, in hydraulic systems and continuous fluid flow systems.
  • servo valves include a movable piston in a housing actuated by a movable flapper.
  • a fluid control apparatus in a first aspect, includes a servo valve with a valve housing having an axial bore extending between a first end and a second end, a first inlet port in fluid communication with the axial bore, and a first outlet port in fluid communication with the axial bore, and a piston located within the axial bore and having a first fluid passage and configured to allow reciprocal axial movement of the piston within the axial bore between a first position in which the first fluid passage aligns axially with the first inlet port and the first outlet port to form a first fluidic circuit in the first position, and a second position in which the piston blocks at least one of the first inlet port and the first outlet port.
  • the apparatus also includes a lockout assembly configurable to fix the piston into a selected position in a first configuration, and not interfere with reciprocal axial movement of the piston in a second configuration.
  • a fluid control apparatus in a second aspect, includes a valve having an inlet port in fluid communication with a control fluid source and an outlet port, the valve being configured to control a flow of fluid from the inlet port to the outlet port, a reference fluid source configured to provide a reference fluid at a predetermined reference pressure and flow, a fluid actuator having a fluid chamber, and a lockout assembly having a valve configurable to a first configuration providing a fluid path from the outlet port to the fluid chamber, and a second configuration providing a fluid path from the reference fluid source to the fluid chamber.
  • a method of controlling a fluid flow includes providing a servo valve having a valve housing having an axial bore extending between a first end and a second end, a first inlet port in fluid communication with the axial bore, and a first outlet port in fluid communication with the axial bore, a piston located within the axial bore and having a first fluid passage and configured to allow reciprocal axial movement of the piston within the axial bore between a first position in which the first fluid passage aligns axially with the first inlet port and the first outlet port to form a first fluidic circuit in the first position, and a second position in which the piston blocks at least one of the first inlet port and the first outlet port.
  • the method also includes providing a lockout assembly configurable to fix the piston into a selected position in a first configuration, and not interfere with reciprocal axial movement of the piston in a second configuration, actuating the lockout assembly into the first configuration, and fixing, by the lockout assembly, the piston into a selected position.
  • the selected position can be the first position.
  • the selected position can be the second position.
  • the lockout assembly can also include a lock operable to prevent disengagement of the lockout assembly from at least one of the first configuration and the second configuration.
  • the lockout assembly can include a stop configurable to contact the piston in the first configuration and not contact the piston in the second configuration.
  • the stop can be disposed at an axial end of the piston.
  • the stop can include a cam, the first configuration can include a first rotary position of the cam, and the second configuration can include a second rotary position of the cam.
  • the lockout assembly can also include a support coupled to the valve housing and having a threaded bore therein, the stop can also include a fastener threadedly engaged with the threaded bore, the first configuration can include threading the fastener through the threaded bore so as to contact the piston, and the second configuration can include threading the fastener through the threaded bore so as to not contact the piston.
  • the valve housing can also include a fluid chamber at one of the first end or the second end, the piston can also include an axial piston end forming a moveable portion of the fluid chamber, the piston being axially moveable to the selected position by fluidic pressure applied to the axial piston end.
  • the fluid chamber can be in fluidic communication with a second inlet port and a second outlet port
  • the lockout assembly can include an outlet valve in fluidic communication with the second outlet port
  • the first configuration can permit the pressurized fluid to flow out of the fluid chamber
  • the second configuration can prevent flow of the pressurized fluid from the fluid chamber.
  • the second inlet port can be in fluidic
  • the lockout assembly can include a stop configurable to extend through the fluid chamber and contact the axial piston end in the first configuration and not contact the axial piston end in the second configuration.
  • the piston can be fluidly connected on a first end to a first fluid pressure chamber and fluidly connected on a second end to a second fluid pressure chamber, the piston configured for reciprocal axial movement in response to a pressure differential between a first fluid in the first fluid pressure chamber and a second fluid in the second fluid pressure chamber
  • the servo valve can also include a flapper assembly including an activation portion and closure portion, said closure portion of the flapper assembly extending from the activation portion, said flapper assembly configured to move said closure portion to engage a first fluid flow control element on the first fluid pressure chamber when the closure portion is in a first closure position and configured to move said closure portion to engage a second fluid flow control element on the second fluid pressure chamber when the closure portion is in a second closure position
  • the lockout assembly can include a stop configurable to fix the activation portion in a selected activation position in the first configuration and not interfere with movement of the activation portion in the second configuration.
  • the selected activation position can position the closure to a selected closure position.
  • the selected closure position can be the first closure position.
  • the selected closure position can be the second closure position.
  • the lockout assembly can also include a support coupled to the valve housing and having a threaded bore therein, the stop can also include a fastener threadedly engaged with the threaded bore, the first configuration can include threading the fastener through the threaded bore so as to contact the activation portion, and the second configuration can include threading the fastener through the threaded bore so as to not contact the activation portion.
  • the apparatus can also include a fluid actuator having a stator portion, an actuator portion, and a fluid chamber between the stator portion and the actuator portion, the fluid chamber in fluid communication with the first outlet.
  • the apparatus can also include a high-capacity fluid valve having a fluid control portion coupled to the actuator portion. The fluid control portion can be operable to control a flow of fluid to an aircraft component.
  • Embodiments of the first aspect, the second aspect, and the third aspect can also include locking the lockout assembly into the first configuration, wherein the lockout assembly further comprises a lock operable to prevent disengagement of the lockout assembly from the first configuration.
  • the selected position can be the first position.
  • the selected position can be the second position.
  • the lockout assembly can be actuated into the second configuration, and, the piston can be released, by the lockout assembly, from being fixed in the selected position such that the lockout assembly does not interfere with reciprocal axial movement of the piston.
  • the lockout assembly can be locked into the second configuration, wherein the lockout assembly further comprises a lock operable to prevent disengagement of the lockout assembly from the second configuration.
  • the piston can be contacted with a stop, wherein the lockout assembly can include the stop, the stop being configurable to contact the piston in the first configuration and not contact the piston in the second configuration.
  • the stop can include a cam
  • the first configuration can include a first rotary position of the cam
  • the second configuration can include a second rotary position of the cam.
  • the lockout assembly can also include a support coupled to the valve housing and having a threaded bore therein
  • the stop can include a fastener threadedly engaged with the threaded bore
  • contacting the piston with the stop can also include threading the fastener through the threaded bore so as to contact the piston.
  • the valve housing can include a fluid chamber at one of the first end or the second end, the piston can also include an axial piston end forming a moveable portion of the fluid chamber, the piston being axially moveable to the selected position by fluidic pressure applied to the axial piston end.
  • the fluid chamber can be in fluidic communication with a second inlet port and a second outlet port, the lockout assembly can include an outlet valve in fluidic communication with the second outlet port, and actuating the lockout assembly into the second configuration can also include preventing flow of the pressurized fluid from the fluid chamber.
  • the second inlet port can be in fluidic communication with a pressurized fluid
  • the lockout assembly can be actuated into the first configuration by a method that includes permitting a threshold fluid pressure within the fluid chamber sufficient to urge the piston into the selected position, and actuating the lockout assembly into the second configuration can include relieving the fluid pressure within the fluid chamber below the threshold fluid pressure.
  • the lockout assembly can include a stop configurable to extend through the fluid chamber and contact the axial piston end in the first configuration and not contact the axial piston end in the second configuration.
  • the piston can be fluidly connected on a first end to a first fluid pressure chamber and fluidly connected on a second end to a second fluid pressure chamber, the piston configured for reciprocal axial movement in response to a pressure differential between a first fluid in the first fluid pressure chamber and a second fluid in the second fluid pressure chamber
  • the servo valve can also include a flapper assembly including an activation portion and closure portion, said closure portion of the flapper assembly extending from the activation portion, said flapper assembly configured to move said closure portion to engage a first fluid flow control element on the first fluid pressure chamber when the closure portion is in a first closure position and configured to move said closure portion to engage a second fluid flow control element on the second fluid pressure chamber when the closure portion is in a second closure position
  • the lockout assembly can include a stop configurable to fix the activation portion in a selected activation position in the first configuration and not interfere with movement of the activation portion in the second
  • the selected activation position can position the closure to a selected closure position.
  • the selected closure position can be the first closure position.
  • the selected closure position can be the second closure position.
  • the lockout assembly can also include a support coupled to the valve housing and having a threaded bore therein, the stop can include a fastener threadedly engaged with the threaded bore, actuating the lockout assembly into the first configuration can include threading the fastener through the threaded bore so as to contact the activation portion.
  • a fluid actuator having a stator portion, an actuator portion, and a fluid chamber between the stator portion and the actuator portion can be provided. The fluid chamber can be in fluid communication with the first outlet. In response to fixing the piston into the selected position, the fluid actuator can be fixed into a selected fluid actuator position.
  • a high-capacity fluid valve having a fluid control portion coupled to the actuator portion can be provided, and, in response to fixing the actuator into the selected actuator position, the high-capacity fluid valve can be fixed into a selected valve position.
  • the fluid control portion can be operable to control a flow of fluid to an aircraft component.
  • the lockout assembly can include a valve.
  • a fluid pressure source can be provided, the valve can be configured into a first configuration, a fluid path can be provided from the first outlet port to the fluid chamber, the valve can be configured into a second configuration, a fluid path can be provided from the fluid pressure source to the fluid chamber.
  • a system can provide hydraulic lockout control over an aircraft component in implementations in which conventional mechanical lockout control is currently used.
  • the system can provide remote lockout control over hydraulic components.
  • the system can provide hydraulic lockout control over an aircraft component with a reduced weight relative to mechanical lockout controls.
  • the system can provide hydraulic lockout control over an aircraft component with a reduced cost relative to mechanical lockout controls.
  • the system can provide hydraulic lockout control over an aircraft component with a reduced size relative to mechanical lockout controls.
  • the system can be retrofitted into applications that currently lack lockout control or implement mechanical lockout control.
  • FIGs. 1 A and 1 B are cross-sectional views of an example servo valve with an example lockout assembly in an unlocked configuration and a locked-out configuration, respectively.
  • FIGs. 2A-2D are cross-sectional views of another example servo valve with another example lockout assembly in an unlocked configuration and a locked-out configuration, respectively.
  • FIGs. 3A and 3B are cross-sectional views of an example electrohydraulic servo valve with an example lockout assembly in an unlocked configuration and a locked-out configuration, respectively.
  • FIGs. 4A and 4B are cross-sectional views of another example electrohydraulic servo valve with another example lockout assembly in an unlocked configuration and a locked-out configuration, respectively.
  • FIG. 5 is a diagram of an example multi-stage fluid control system with an example lockout assembly.
  • FIG. 6 is a diagram of an example multi-stage fluid control system with an example line-replaceable unit lockout assembly.
  • FIGs. 7A and 7B are diagrams of another example multi-stage fluid control system with an example line-replaceable unit lockout assembly.
  • FIG. 8 is a flow diagram of an example process for locking out a hydraulic actuator servo valve.
  • Servo valves are sometimes used as part of a multi-stage apparatus configured to control the flows of fluids at pressures and/or flow rates that are too great to be controlled by the servo valve directly.
  • the servo valve may be used as a first stage to control the flow of fluid to a linear, or rotary, fluid actuator second stage used to amplify the fluid force of the servo and actuate a regulator (e.g., valve, nozzle) for controlling the flow of a controlled fluid.
  • a regulator e.g., valve, nozzle
  • a multi-stage apparatus may be normally used in the operation of a less-critical aircraft function, but nevertheless a malfunction of the servo valve or the system controlling the servo valve may require the plane to remain grounded until the malfunction can be overridden or repaired.
  • the aircraft may be made airworthy again by temporarily overriding the operation of the servo valve and locking the regulator (e.g., valve, nozzle) of the controlled fluid in a closed, wide open, or other predetermined position.
  • the multi-stage apparatus may be used to control a flow of air to cool a jet engine, in which excess heat may damage the engine, while excess cooling may only cause the engine to run at less than peak fuel efficiency without any additional safety concerns. If a servo valve without a lockout apparatus malfunctions in such an application, the engine may overheat and present a danger requiring the aircraft to remain grounded until the malfunction can be diagnosed and repaired.
  • the apparatus may be temporarily locked-out to cause (in this particular example) the cooling air flow to be locked away from a configuration that could cause a potentially dangerous overheat condition, and into a configuration that errs on the side of safety in which the engine is overcooled and less efficient, but otherwise safe to operate.
  • the use of a servo valve with a lockout apparatus may be used to reduce the amount of time needed to return an aircraft or other application to operational status.
  • the controlled fluid, the fluid regulator, and/or the second stage fluid actuator may be in a location that is difficult or time consuming to access (e.g., to repair or to lock out directly).
  • the servo valve of the first stage may be located remotely from the second stage, in a location that is more quickly and easily accessed.
  • the lockout apparatus may be located behind an access panel and may be secured in the locked-out configuration in a matter of minutes using only a technician's hands and/or basic tools.
  • a plane In commercial aircraft applications, by locking out a non-critical function, a plane may be able to be able to complete a flight or be flown to a repair facility. In military aircraft applications, by locking out a non-critical function, a plane may be returned to service quickly or a battle-damaged plane may be "limped" back to safe territory.
  • FIGs. 1 A and 1 B are cross-sectional views of an example servo valve 100 with an example lockout assembly 150 in an unlocked configuration and a locked-out configuration, respectively.
  • the servo valve 100 includes a piston housing 104, a piston 108 disposed in a chamber 1 19 of the housing 104, and a fluid chamber housing 1 10.
  • the piston 108 is fluidly connected on a first end 1 16 to a first fluid pressure chamber 1 18, and the piston 108 is fluidly connected on a second end 138 to a second fluid pressure chamber 139.
  • the piston 108 is configured to translate axially within the housing 104 in response to a pressure of a first fluid in the first fluid pressure chamber 1 18 and/or the pressure of a second fluid in the second fluid pressure chamber 139.
  • the cross-sectional shape of the piston 108 and housing 104 can vary.
  • the piston 108 and the housing 104 can each have a rectangular, square, circular, ovoid or different cross-sectional shape.
  • the piston 108 has the same, or substantially the same, cross sectional shape as the housing 104 such that a pressure seal can exist between the piston 108 and the housing 104 while allowing translative movement of the piston 108 within the chamber 1 19. In the example shown in FIGs.
  • the piston 108 is substantially cylindrical with a circular cross-sectional shape that matches (substantially or wholly) a substantially cylindrical inner sidewall forming a chamber configured to allow translatable motion of the piston 108 within the housing 104.
  • the piston 108 includes an outer groove 130a and an outer groove 130b disposed circumferentially in a substantially cylindrical outer surface of the piston 108.
  • the housing 104 includes an opening 132a and an opening 132b in the sidewall of the housing 104 fluidically connected to a high pressure fluid pathway, an opening 136a and an opening 136b in the sidewall of the housing 104 fluidically connected to a low pressure fluid pathway, an opening 140a in the sidewall of the housing 104 fluidically connected to a first output fluid pathway and an opening 140b in the sidewall of the housing 104 fluidically connected to a second output fluid pathway.
  • the opening 140a is positioned in the housing 104 such that when the groove 130a in the piston 108 translates as the piston 108 moves axially, fluid in the groove 130a remains in fluid communication with the opening 140a.
  • the opening 132a to the high pressure fluid pathway is spaced apart from and positioned in the sidewall to a first side of the opening 140a
  • the opening 136a to the low pressure fluid pathway is spaced apart from and positioned in the sidewall to a second side of the opening 140a to the output fluid pathway in an opposite axial direction from the opening 132a to the high pressure fluid pathway.
  • the opening 140b is positioned in the housing 104 such that when the groove 130b in the piston 108 translates as the piston 108 moves axially, fluid in the groove 130b remains in fluid communication with the opening 140b.
  • the opening 132b to the high pressure fluid pathway is spaced apart from and positioned in the sidewall to a first side of the opening 140b
  • the opening 136b to the low pressure fluid pathway is spaced apart from and positioned in the sidewall to a second side of the opening 140b to the output fluid pathway in an opposite axial direction from the opening 132b to the high pressure fluid pathway.
  • the opening 132a to the high pressure fluid pathway is positioned in the housing 104 such that when the groove 130a in the piston 108 translates as the piston 108 moves axially in a first direction, fluid in the groove 130a remains in fluid communication with the opening 136a to the low pressure fluid pathway and an outer surface of the piston 108 closes the opening 132a to the high pressure fluid pathway.
  • the opening 132a to the high pressure fluid pathway is positioned in the housing 104 such that when the groove 130a in the piston 108 translates as the piston 108 moves axially in a second direction opposite the first direction, fluid in the groove 130a remains in fluid
  • the opening 132b to the high pressure fluid pathway is positioned in the housing 104 such that when the groove 130b in the piston 108 translates as the piston 108 moves axially in the second direction, fluid in the groove 130b remains in fluid communication with the opening 136b to the low pressure fluid pathway and an outer surface of the piston 108 closes the opening 132b to the high pressure fluid pathway.
  • the opening 132b to the high pressure fluid pathway is positioned in the housing 104 such that when the groove 130b in the piston 108 translates as the piston 108 moves axially in the first direction opposite the second direction, fluid in the groove 130b remains in fluid communication with the opening 132b to the high pressure fluid pathway and an outer surface of the piston 108 closes the opening 136b to the low pressure fluid pathway.
  • one or both of the openings 140a and 140b can be fluid outputs.
  • one or both of the openings 140a and 140b can be operably connected to a fluid drive system, for example, a hydraulic actuator (e.g., a linear actuator, a rotary piston actuator, a rotary vane actuator, a fluid motor).
  • the hydraulic actuator may be used to mechanically move an element of a device from a first position to a second position.
  • the hydraulic output may be used to move an object (e.g. piston, actuator, fuel nozzle, etc.) on an aircraft from a first position to a second position and to intermediate positions therebetween.
  • the example servo valve 100 includes the lockout assembly 150.
  • the lockout assembly 150 includes moveable housing end 152 configured to translate axially within the open end 138 the housing 104.
  • a seal 154 provides a fluid seal between the moveable housing end 152 and the open end 138.
  • the lockout assembly 150 also includes a stop in the form of a rotary cam 156 and a lever arm 158.
  • the rotary cam 156 is configured to pivot eccentrically about an axis 157 to selectively partially extend and retract in the axial direction of the moveable housing end 152.
  • the servo valve 100 may be another form of fluid control valve, such as a solenoid valve.
  • the lockout assembly 150 is shown in an unlocked configuration.
  • the rotary cam 156 is positioned such that the eccentricity of the rotary cam 156 causes the rotary cam 156 to extend from the axis 157 substantially away from the open end 138.
  • the moveable housing end 152 is able to translate axially within the open end 138 toward the axis 157 and away from the piston 108.
  • the moveable housing end 152 may be urged into contact with the rotary cam 156 by axial movement of the piston 108.
  • the piston 108 is able to move axially within the housing 104 between the first and second position without mechanical interference from the moveable housing end 152.
  • a receptacle 160a (e.g., a bolt hole) aligns with a bore (not shown) in the lever arm 158.
  • a fastener 162 (e.g., a bolt, set screw) passes through the bore and into the receptacle 160a to reversibly secure the lever arm 158 and the rotary cam 156 in the unlocked configuration.
  • the lockout assembly 150 is shown in a locked configuration.
  • the rotary cam 156 is rotated such that the eccentricity of the rotary cam 156 causes the rotary cam 156 to extend from the axis 157 substantially toward the open end 138.
  • the moveable housing end 152 translate axially within the open end 138 away from the axis 157 and urges the piston 108 into a predetermined one of the first or the second directions.
  • the fastener 162 e.g., a bolt, set screw
  • the piston 108 is mechanically held in a predetermined position.
  • the locked configuration can cause the piston 108 to create a fluid circuit from one or both of the openings 132a-132b (e.g., the high pressure fluid pathway) to the
  • the locked configuration can cause the piston 108 to create a fluid circuit from one or both of the openings 136a-136b (e.g., the low pressure fluid pathway) to the corresponding opening 140a-140b.
  • a supply of high pressure and/or low pressure fluid may be supplied, for example to a fluid actuator, substantially overriding the ability of the servo valve 100 to vary the fluid pressure at one or both of the openings 140a-140b.
  • FIGs. 2A and 2C are cross-sectional views of another example servo valve 200 with another example lockout assembly 250 in an unlocked configuration and a locked-out configuration, respectively.
  • FIGs. 2B and 2D are cross-sectional views of the lockout assembly 250 in an unlocked configuration and a locked-out configuration, respectively, taken across the section identified as A-A.
  • the example servo valve 200 includes the piston housing 104, the piston 108 disposed in the housing 104, and a fluid chamber housing 210.
  • the piston 108 is fluidly connected on the first end 1 16 to the first fluid pressure chamber 1 18, and the piston 108 is fluidly connected on the second end 138 to the second fluid pressure chamber 139.
  • the piston 108 is configured to translate axially within the housing 104 in response to a pressure of a first fluid in the first fluid pressure chamber 1 18 and/or the pressure of a second fluid in the second fluid pressure chamber 139.
  • the fluid chamber housing 210 includes an opening 212 in fluid communication with a fluid path 254.
  • the fluid path 254 can be a fluid inlet through which a pressurized fluid can be applied to pressurize the first fluid pressure chamber 1 18 to urge movement of the piston 108.
  • the fluid path 254 can be a fluid outlet through which a pressurized fluid can escape the first fluid pressure chamber 1 18 to permit movement of the piston 108.
  • the first fluid pressure chamber 1 18 can be fluidly connected to the opening 132a and/or 132b, such that a supply of high pressure fluid can flow into and pressurize the first fluid chamber 1 18 to urge movement of the piston 108.
  • one or both of the openings 140a and 140b can be fluid outputs.
  • one or both of the openings 140a and 140b can be operably connected to a fluid drive system, for example, a hydraulic actuator (e.g., a linear actuator, a rotary piston actuator, a rotary vane actuator, fluid motor).
  • a hydraulic actuator e.g., a linear actuator, a rotary piston actuator, a rotary vane actuator, fluid motor.
  • the hydraulic actuator may be used to
  • the servo valve 200 includes the lockout assembly 250.
  • the lockout assembly 250 includes a valve housing 252 and a valve 256.
  • the valve 256 is configured to selectively open or block the fluid path 254.
  • a lever arm 258 is connected to and configured to open and close the valve 256.
  • the example servo valve 200 is shown in an unlocked configuration.
  • the valve 256 is positioned to permit a fluid flow through the fluid path 254.
  • fluid in the first fluid chamber 1 18 can escape through the fluid path 254 as the first end 1 16 of the piston 108 is urged into the fluid chamber housing 210.
  • a receptacle 260a e.g., a bolt hole
  • a fastener 262 passes through the bore and into the receptacle 260a to reversibly secure the lever arm 258 and the valve 256 in the unlocked configuration.
  • the example lockout assembly 250 is shown in a locked configuration.
  • the valve 256 is positioned to block a fluid flow through the fluid path 254.
  • fluid in the first fluid chamber 1 18 cannot escape through the fluid path 254 as the first end 1 16 of the piston 108 is urged into the fluid chamber housing 210.
  • the first fluid chamber 1 18 may be in fluid communication with a high pressure fluid path, e.g., though the openings 132a or 132b.
  • fluid pressure will build up within the first fluid chamber 1 18 since the fluid path 254 is blocked, and the pressure will urge movement of the first end 1 16 partly away from the fluid chamber housing 210 and hold the piston 108 in that position hydraulically until the lockout assembly 250 is reconfigured to the unlocked configuration.
  • the openings 140a and/or 104b may be kept at a preselected one of high pressure or low pressure.
  • the fastener 262 e.g., a bolt, set screw
  • FIGs. 3A and 3B are cross-sectional views of an example electrohydraulic servo valve (“EHSV") 300 with an example lockout assembly 380 in an unlocked configuration and a locked-out configuration, respectively.
  • the EHSV 300 includes a valve housing 302, a piston cylinder 304, a piston 308 disposed in the cylinder 304, and a flapper assembly 310 with an activation portion 312 and a closure portion 314.
  • the activation portion 312 is substantially enclosed within a housing 31 1 .
  • the sleeve 306 is not a required element for implementation of this disclosure.
  • the piston 308 may be disposed directly in a bore of the piston cylinder 304.
  • the piston 308 is fluidly connected on a first end to a first fluid pressure chamber 316, and is fluidly connected on a second end to a second fluid pressure chamber 318.
  • the piston 308 is configured to translate axially within the sleeve 306 in response to a pressure differential between a first fluid in the first fluid pressure chamber 316 and a second fluid in the second fluid pressure chamber 318.
  • the closure portion 314 of the flapper assembly 310 extends from the activation portion 312, and the flapper assembly 310 is configured to move the closure portion 314.
  • the flapper assembly 310 is configured to move the closure portion 314 to engage a first fluid flow control element 320 on the first fluid pressure chamber 316 when the closure portion 314 is in a first position, and is configured to move the closure portion 314 to engage a second fluid flow control element 322 on the second fluid pressure chamber 318 when the closure portion 314 is in a second position.
  • the first fluid flow control element 320 includes a first nozzle in the first fluid pressure chamber 316
  • the second fluid flow control element 322 includes a second nozzle in the second fluid pressure chamber 318.
  • the first nozzle is configured to seal against the closure portion 314 of the flapper assembly 310 when the closure portion 314 engages with the first nozzle in the first position.
  • the second nozzle is configured to seal against the closure portion 314 of the flapper assembly 310 when the closure portion 314 engages with the second nozzle in the second position.
  • the fluid flow control elements 320 and 322 include other, different flow control features.
  • the activation portion 312 of the flapper assembly 310 can be implemented in various manners.
  • the activation portion 312 can include a pressure activated diaphragm, a linear actuator, a pneumatic actuator, a servo motor, an armature with electrified coils about ends of the armature, and/or a different activation component.
  • the example EHSV 300 includes two electrical coils 324 disposed proximal to the activation portion 312 of the flapper assembly 310.
  • the flapper assembly 310 is movably attached to the housing 302, for example, by a pivot spring 326 configured to resist rotation of the flapper assembly 310. In the example shown in FIGs.
  • the two electrical coils 324 coil about opposite ends of the activation portion 312.
  • an electrical input such as an input voltage or current
  • the electrical coils 324 produces an electromagnetic force that results in a torque acting on the activation portion 312 to rotate the closure portion 314 to a specific position.
  • the pivot spring 326 is configured to resist rotation of the flapper assembly 310 while the electrical coils 324 promote rotation of the flapper assembly 310, such that the rotation of the flapper assembly 310 is proportional to the electrical input to the electrical coils 324.
  • the example EHSV 300 can include a different number of coils 324, for example, one coil, or three or more coils.
  • the coils 324 can include a solenoid, coiled copper wire, and/or other electrical components.
  • the EHSV 300 includes a feedback spring 328 connected to the closure portion 314 of the flapper assembly 310 on one end and the piston 308 on another end.
  • the feedback spring 328 is configured to provide a force balance between the piston 308 and the flapper assembly 310.
  • the piston 308 translates until torque on the flapper assembly 310 from the feedback spring 328 balances torque on the flapper assembly 310 applied by the electrical input of the electrical coils 324.
  • an outer periphery portion of the piston 308 pressure-seals against an inner surface of the sleeve 306 such that the first fluid in the first fluid pressure chamber 316 is separated from the second fluid in the second fluid pressure chamber 318.
  • peripheries of the opposite ends of the piston 308 can seal against the sleeve 306 such that the first fluid is retained on one end of the sleeve 306 against a first end of the piston 308, and the second fluid is retained on an opposite end of the sleeve 306 against a second, opposite end of the piston 308.
  • Pressure differentials between the first fluid and the second fluid can actuate the piston 308 to translate within the sleeve 306.
  • the cross-sectional shape of the piston 308 and sleeve 306 can vary.
  • the piston 308 and sleeve 306 can each have a
  • the piston 308 has the same, or substantially, the same, cross sectional shape as the sleeve 306 such that a pressure seal can exist between the piston and the sleeve while allowing translative movement of the piston 308 within the sleeve 306.
  • the piston cylinder 304 will be configured with a cross-section to slidably receive the piston 308 of a non-cylindrical cross-section.
  • the piston 308 is substantially cylindrical with a circular cross-sectional shape that matches (substantially or wholly) a substantially cylindrical inner sidewall of the sleeve 306.
  • the piston 308 includes an outer groove 330 disposed
  • the sleeve 306 includes an opening 332 in the sidewall of the sleeve 306 fluidically connected to a high pressure fluid pathway 334, an opening 336 in the sidewall of the sleeve 306 fluidically connected to a low pressure fluid pathway 338, and an opening 340 in the sidewall of the sleeve 306 fluidically connected to an output fluid pathway 342.
  • the opening 340 to the output fluid pathway 342 is positioned in the sleeve 306 such that when the groove 330 in the piston 308 translates as the piston 308 moves axially, fluid in the groove 330 remains in fluid communication with the opening 340 to the output fluid pathway 342.
  • the opening 332 to the high pressure fluid pathway 334 is spaced apart from and positioned in the sidewall to a first side of the opening 340 to the output fluid pathway 342, and the opening 336 to the low pressure fluid pathway 338 is spaced apart from and positioned in the sidewall to a second side of the opening 340 to the output fluid pathway 342 in an opposite axial direction from the opening 332 to the high pressure fluid pathway 334.
  • the opening 332 to the high pressure fluid pathway 334 is positioned in the sleeve 306 such that when the groove 330 in the piston 308 translates as the piston 308 moves axially in a first direction, fluid in the groove 330 remains in fluid communication with the opening 336 to the low pressure fluid pathway 338 and an outer surface of the piston 308 closes the opening 332 to the high pressure fluid pathway 334 (See FIG. 3B).
  • the opening 336 to the high pressure fluid pathway 334 is positioned in the sleeve 306 such that when the groove 330 in the piston 308 translates as the piston 308 moves axially in a second direction opposite the first direction, fluid in the groove 330 remains in fluid communication with the opening 332 to the high pressure fluid pathway 334 and an outer surface of the piston 308 closes the opening 336 to the low pressure fluid pathway 338.
  • the output fluid pathway 342 can be operably connected to a fluid drive system, for example, a hydraulic actuator.
  • the hydraulic actuator may be used to mechanically move an element of a device from a first position to a second position.
  • the hydraulic output may be used to move an object (e.g. piston, actuator, fuel nozzle, etc.) on an aircraft from a first position to a second position and to intermediate positions there between.
  • the first fluid pressure chamber 316 is connected on one end to the high pressure fluid pathway 334 via a first pressure change element 354, and connected on another end to the low pressure fluid pathway 338 via the first fluid flow control element 320.
  • the second fluid pressure chamber 318 is connected on one end to the high pressure fluid pathway 334 via a second pressure change element 356 and on another end to the low pressure fluid pathway 338 via the second fluid flow control element 322, with an intermediate section extending into the sleeve 306 proximate the second end of the piston 308.
  • the first pressure change element 354 regulates pressure between fluid in the high pressure fluid pathway 334 and fluid in the first fluid pressure chamber 316 based on fluid flow through the first pressure change element 354.
  • the first fluid flow control element 320 regulates pressure between fluid in the low pressure fluid pathway 338 and fluid in the first fluid pressure chamber 316.
  • the first pressure change element 354 creates a pressure drop between the high pressure fluid pathway 334 and first fluid pressure chamber 316
  • the first fluid flow control element 320 creates a pressure drop between the first fluid pressure chamber 316 and the low pressure fluid pathway 338, such that fluid in the first fluid pressure chamber 316 is at an intermediate pressure between the higher pressure in the high pressure fluid pathway 334 and the lower pressure in the low pressure fluid pathway 338.
  • the second pressure change element 356 regulates pressure between fluid in the high pressure fluid pathway 334 and fluid in the second fluid pressure chamber 318 based on fluid flow through the second pressure change element 356.
  • the second fluid flow control element 322 regulates pressure between fluid in the low pressure fluid pathway 338 and fluid in the second fluid pressure chamber 318.
  • the second pressure change element 356 creates a pressure drop between the high pressure fluid pathway 334 and second fluid pressure chamber 318
  • the second fluid flow control element 322 creates a pressure drop between the second fluid pressure chamber 318 and the low pressure fluid pathway 338, such that fluid in the second fluid pressure chamber 318 is at an intermediate pressure between the higher pressure in the high pressure fluid pathway 334 and the lower pressure in the low pressure fluid pathway 338.
  • the first pressure change element 354 and second pressure change element 356 can each include a hydraulic bridge with an orifice, where the orifice is adapted to regulate pressure based on fluid flow through the orifice, for example, fluid flow from the high pressure fluid pathway 334 through the orifice and to the first fluid pressure chamber 316, or fluid flow from the high pressure fluid pathway 334 through the orifice and to the second fluid pressure chamber 318.
  • the lockout assembly 380 includes a bore 382 formed in the housing 31 1 .
  • a stop 384 in the form of a rod, bolt, or any other appropriate shape can be passed through the bore 382 to contact the flapper assembly 310.
  • the bore 382 may be threaded and the stop 384 may be a bolt threaded to mate with the bore 382, and the stop 384 may be threaded into and out of the bore 382 to reversibly bring the stop 384 into and out of contact with the flapper assembly 310.
  • the stop 384 is configured to contact the activation portion 312. In some embodiments, the stop 384 can be configured to contact the closure portion 314.
  • the example lockout assembly 380 is shown in an unlocked configuration. In the unlocked configuration, the stop 384 does not interfere with the operation of the flapper assembly 310.
  • the example lockout assembly 380 is shown in a locked configuration.
  • the stop 384 contacts the flapper assembly 310.
  • the stop 384 mechanically interferes with the ability of the flapper assembly 310 to move.
  • the stop 384 reversibly fixes the flapper assembly 310 in a position such that the closure portion 314 engages a selected one of the first fluid control element 320 or the second fluid control element 322.
  • the stop 384 contacts the activation portion 310 to urge the closure portion 314 into the first position and engage the first fluid control element 320.
  • Fluid in the groove 330 remains in fluid communication with the opening 336 to the low pressure fluid pathway 338 and an outer surface of the piston 308 closes the opening 332 to the high pressure fluid pathway 334.
  • the opening 336 to the high pressure fluid pathway 334 is positioned in the sleeve 306 such that when the groove 330 in the piston 308 translates as the piston 308 moves axially in a second direction opposite the first direction, fluid in the groove 330 remains in fluid communication with the opening 332 to the high pressure fluid pathway 334 and an outer surface of the piston 308 closes the opening 336 to the low pressure fluid pathway 338.
  • the output fluid pathway 342 can be operably connected to a fluid drive system, for example, a hydraulic actuator.
  • a fluid drive system for example, a hydraulic actuator.
  • the action of the servo valve may be selectably overridden to cause a selected high or low pressure fluid to be applied to the fluid drive system, which in turn can be used to urge the fluid drive system into a reversibly fixed mechanical position.
  • FIGs. 4A and 4B are cross-sectional views of another example electrohydraulic servo valve (“EHSV") 400 with another example lockout assembly 480 in an unlocked configuration and a locked-out configuration, respectively.
  • the EHSV 400 includes a valve housing 402, a piston cylinder 404, the piston 308 of FIGs.
  • the piston 308 is fluidly connected on a first end to a first fluid pressure chamber 316, and is fluidly connected on a second end to a second fluid pressure chamber 318.
  • the piston 308 is configured to translate axially within the sleeve 306 in response to a pressure differential between a first fluid in a first fluid pressure chamber 416 and a second fluid in a second fluid pressure chamber 418.
  • the piston cylinder 404 includes the opening 332 in the sidewall of the piston cylinder 404 fluidically connected to the high pressure fluid pathway 334, the opening 336 in the sidewall of the piston cylinder 404 fluidically connected to a low pressure fluid pathway 338, and the opening 340 in the sidewall of the piston cylinder 404 fluidically connected to the output fluid pathway 342.
  • the opening 340 to the output fluid pathway 342 is positioned in the piston cylinder 404 such that when the groove 330 in the piston 308 translates as the piston 308 moves axially, fluid in the groove 330 remains in fluid communication with the opening 340 to the output fluid pathway 342.
  • the opening 332 to the high pressure fluid pathway 334 is spaced apart from and positioned in the sidewall to a first side of the opening 340 to the output fluid pathway 342, and the opening 336 to the low pressure fluid pathway 338 is spaced apart from and positioned in the sidewall to a second side of the opening 340 to the output fluid pathway 342 in an opposite axial direction from the opening 332 to the high pressure fluid pathway 334.
  • the opening 332 to the high pressure fluid pathway 334 is positioned in the sleeve 306 such that when the groove 330 in the piston 308 translates as the piston 308 moves axially in a first direction, fluid in the groove 330 remains in fluid
  • the opening 336 to the high pressure fluid pathway 334 is positioned in the sleeve 306 such that when the groove 330 in the piston 308 translates as the piston 308 moves axially in a second direction opposite the first direction, fluid in the groove 330 remains in fluid communication with the opening 332 to the high pressure fluid pathway 334 and an outer surface of the piston 308 closes the opening 336 to the low pressure fluid pathway 338.
  • the output fluid pathway 342 can be operably connected to a fluid drive system, for example, a hydraulic actuator.
  • the hydraulic actuator may be used to mechanically move an element of a device from a first position to a second position.
  • the hydraulic output may be used to move an object (e.g. piston, actuator, fuel nozzle, etc.) on an aircraft from a first position to a second position and to intermediate positions there between.
  • the example lockout assembly 480 includes a bore 482 formed in and end cap 41 1 which provides a wall of the first fluid pressure chamber 416.
  • a stop 484 in the form of a rod, bolt, set screw, or any other appropriate shape can be passed through the bore 482 and the first fluid pressure chamber 416 to contact the piston 308.
  • the bore 482 may be threaded and the stop 484 may be a bolt threaded to mate with the bore 482, and the stop 484 may be threaded into and out of the bore 482 to reversibly bring the stop 484 into and out of contact with the piston 408.
  • a seal may be provided between the stop 484 and the bore 482 to resist leakage of fluid from the first fluid pressure chamber 416.
  • the example lockout assembly 480 is shown in an unlocked configuration. In the unlocked configuration, the stop 484 does not interfere with the axial translation of the piston 408.
  • the example lockout assembly 480 is shown in a locked configuration.
  • the stop 484 contacts the piston 408, urging the piston 408 in the first direction and reversibly fixing the piston 408 at a predetermined axial position.
  • the stop 484 When in contact with the piston 408, the stop 484 mechanically interferes with the ability of the piston 408 to move.
  • the stop 484 reversibly fixes the piston 408 in the first direction such that low pressure fluid pathway 338 is in fluidic communication with the output fluid pathway 342 through the groove 330.
  • the lock assembly 480 can be configured to reversibly fix the piston 408 in the second direction.
  • the lock assembly 480 and the EHSV 400 can be configured to provide high pressure fluid at the output fluid pathway 342 when in the locked configuration.
  • the lock assembly 480 and the EHSV 400 can be configured to provide low pressure fluid at the output fluid pathway 342 when in the locked configuration.
  • the lockout assembly 480 can have other forms.
  • the lockout assembly 150 of FIGs. 1 A-1 B may be used in place of the lockout assembly 480.
  • the lockout assembly 150 of the servo valve 100 may be replaced with the lockout assembly 480.
  • FIG. 5 is a diagram of an example multi-stage fluid control system 500 with an example lockout assembly.
  • the system 500 includes the servo valve 100 of FIGs. 1A-1 B, which includes the lockout assembly 150.
  • the servo valve 100 and the lockout assembly 150 can be substituted in the system 500 by any of the servo valve 200 and the lockout assembly 250 of FIGs. 2A-2D, the EHSV 300 and the lockout assembly 380 of FIGs. 3A-3B, the EHSV of FIGs. 4A-4B and the lockout assembly 480, or any appropriate combination of servo valves 100, 200, 300, 400 and the lockout assemblies 150, 250, 380, 480.
  • the servo valve 100 is configured as a fluid control device, which provides fluids at controllably variable pressures to a fluid actuator 510 through a fluid conduit 512a and a fluid conduit 512b.
  • the fluid actuator 510 includes a stator portion 520 and an actuator portion 522.
  • the actuator portion 522 is configured to actuate a fluid control apparatus 550.
  • the fluid control apparatus 550 is configured to control a flow of fluids, represented by the arrow 552, flowing through a conduit 554 at a pressure, temperature, and/or rate that is too high for the servo valve 100 to control directly.
  • the fluid actuator 510 amplifies the fluid power provided by the servo valve 100.
  • some servo valve designs are not well-suited for controlling high fluid flow, high fluid temperature, or high fluid pressure applications directly.
  • a servo valve can provide a relatively lower pressure fluid supply to an external fluid actuator such as the actuator 510, the action of which can be used to operate the fluid control apparatus 550.
  • the servo valve 100 operates normally, providing controllably varying fluid pressures to the fluid actuator 510 through the fluid conduits 512a-512b.
  • the varying pressures urge actuation of the actuator 510, and actuation of the actuator 510 urges actuation of the fluid control apparatus 550.
  • the positioning and movement of the piston 108 within the servo valve 100 indirectly controls the position and/or configuration of the fluid control apparatus 550.
  • the operation of the servo valve is overridden to reversibly fix the piston 108 in a predetermined location (e.g., a hard stop at the end of travel in the first direction or the second direction).
  • a predetermined location e.g., a hard stop at the end of travel in the first direction or the second direction.
  • the fluid actuator 510 can be a linear piston actuator, a rotary piston actuator (RPA), a rotary vane actuator (RVA), a fluid motor, or any other appropriate form of fluid actuator.
  • a linear actuator can be urged into a fully extended or fully retracted position.
  • a rotary actuator can be urged to a hard-stopped clockwise or counterclockwise rotational position.
  • a fluid motor can be urged into constant rotation in a predetermined direction.
  • the actuator 510 is actuated (e.g., extended, rotated) in a first direction by an application of a pressurized fluid, provided through the fluid conduit 512a, to a fluid chamber 514.
  • the actuator 510 is actuated in a second direction by an application of a pressurized fluid, provided through the fluid conduit 512b, to a fluid chamber 516.
  • a pressurized fluid provided through the fluid conduit 512b
  • the force used to actuate the actuator 510 in the first or second direction may be provided by a spring, gravity, compressible fluid, or any other appropriate source of mechanical force.
  • the fluid control apparatus 550 can be a fluid valve, a fluid flow regulator, a fluid pressure regulator, a diverter, a manifold, or any other appropriate device that may controllably alter the behavior of a fluid.
  • the fluid actuator 510 can actuate the fluid control apparatus to controllably vary the flow 552 through the conduit 554.
  • the fluid actuator 510 is urged into a predetermined configuration, which in turn urges the fluid control apparatus 550 into a predetermined configuration.
  • the locked configuration may cause the fluid control apparatus 550 be configured in a substantially “wide open” (e.g., full pressure and/or flow) or "closed shut” in which the flow 552 through the conduit 554 is substantially blocked.
  • the locked configuration can cause the fluid control apparatus 550 to be urged into any appropriate fluid flow configuration.
  • the example system 500 may be used in an aircraft or other vehicular application.
  • the servo valve 100 may be used to indirectly control the fluid control apparatus 550 configured to control a rate or pressure of fuel, coolant, air, or other fluids used in the operation of a turbine engine.
  • the system 500 may be used for locking out a remotely located engine or other function or apparatus.
  • the fluid actuator 510, the conduit 554, and/or the fluid control apparatus 550 e.g., a valve
  • the fluid control apparatus 550 may be located deep within a complex assembly such as a jet engine.
  • the servo valve 100 and the lockout assembly 150 configured as the fluid control device of the system 100, may be located remotely from the fluid actuator 510, the conduit 554, and/or the fluid control apparatus 550.
  • the servo valve 100 and the lockout assembly 150 may be located behind a service panel on the exterior of an aircraft and can be easily accessed by a ground crew.
  • the servo valve 100 and the lockout assembly 150 may be located behind an access panel in the interior of an aircraft and can be easily accessed by the flight crew (e.g., to lock out a function in mid-flight). In these and other examples, the servo valve 100 may be located relatively far away from the fluid actuator 510, fluidically connected by the fluid conduits 512a-512b.
  • FIG. 6 is a diagram of an example multi-stage fluid control system 600 with an example line-replaceable unit LRU lockout assembly 620.
  • the LRU 620 provides lockout functionality similar to that provided by the lockout assemblies 150, 250, 380, 480 of FIGs. 1A-5.
  • the LRU 620 can be an assembly that can be retrofitted into existing multi-stage actuator configurations to provide lockout functionality otherwise lacking in such configurations.
  • the example system 600 includes a servo valve 610, the fluid actuator 510, and the fluid control apparatus 550.
  • the fluid chamber 516 is pressurized by fluid provided by a first reference pressure source 630 at a first reference pressure and flow.
  • the first reference pressure and flow can be a predetermined pressure and flow.
  • the first reference pressure and flow can be greater than zero relative pressure and flow.
  • the servo valve 610 may be replaced by a solenoid valve, or any other appropriate form of valve.
  • the fluid chamber 514 is supplied with pressurized fluid flowing through the LRU 620.
  • the LRU is configured to selectively provide the actuator 510 with fluid from the servo valve 610 or from a second reference pressure source 640 at a second reference pressure and flow.
  • the LRU 620 can be a multi-way valve, select valve, or manifold. Under normal operating conditions, the LRU 620 is configured to block fluid pressure provided by the second reference pressure source 640 and pass a controllably variable fluid pressure controlled by the servo valve 610 to the fluid chamber 514.
  • Fluid pressure and flow in the fluid chamber 514 acts against the fluid pressure in the fluid chamber 516, and the fluid actuator 510 will actuate bidirectionally as the pressure of the fluid controlled by the servo valve 610 varies relative to the pressure and flow of the fluid provided by the first reference pressure source 630.
  • the second reference pressure and flow can be a predetermined pressure and flow. In some embodiments, the second reference pressure and flow can be greater than zero relative pressure and flow. In some embodiments, the second reference pressure and flow can be greater than the first reference pressure and flow. In some embodiments, the second reference pressure and flow can be less than the first reference pressure and flow.
  • the LRU 620 may be configured to block fluid pressure and flow provided by the servo valve 610 and pass fluid (e.g., at the second pressure) provided by the second reference pressure source 640 to the fluid chamber 514.
  • the fluid provided by the second reference pressure source 640 will be at a predetermined pressure less than that of the fluid provided by the first reference pressure source 630.
  • the fluid actuator 510 and the fluid control apparatus 550 will be urged in a first direction to a first position, substantially blocking or unblocking the flow 552 through the fluid conduit 554 while the LRU 620 is in the locked-out configuration.
  • the fluid provided by the second reference pressure source 640 will be at a predetermined pressure greater than that of the fluid provided by the first reference pressure source 630.
  • the fluid actuator 510 and the fluid control apparatus 550 will be urged in a second direction opposite of the first direction to a second position, substantially blocking or unblocking the flow 552 through the fluid conduit 554 while the LRU 620 is in the locked-out configuration.
  • the system 600 may be used in an aircraft or other vehicular application.
  • the servo valve 610 may be used to indirectly control the fluid control apparatus 550 configured control a rate or pressure of fuel, coolant, air, or other fluids used in the operation of a turbine engine.
  • the system 600 may be used for locking out a remotely located engine or other function.
  • the servo valve 610, the fluid actuator 510, the conduit 554, and/or the fluid control apparatus 550 e.g., a valve
  • the fluid control apparatus 550 e.g., a valve
  • the LRU 620 may be located remotely from the servo valve 610 and/or the fluid actuator 510, the conduit 554, and/or the fluid control apparatus 550.
  • the LRU 620 may be located in an area that is relatively easy to be accessed by ground or flight crews (e.g., behind an access panel).
  • the servo valve 610 may be a different fluid control apparatus such as a solenoid valve.
  • FIGs. 7A and 7B are diagrams of another example multi-stage fluid control system 700 with an example line-replaceable unit lockout assembly 720.
  • the system 700 can be the system 600 of FIG. 6, and the LRU 720 can be the LRU 620.
  • the system 700 includes a solenoid valve 710, the LRU 720, and a fluid linear actuator 750.
  • the solenoid valve 710 can be substituted with a servo valve or any other appropriate type of fluid valve.
  • the fluid linear actuator 750 can be configured to control the fluid control apparatus 550.
  • the solenoid valve 710 includes a high pressure port 702 connected to a first control fluid source (e.g., high pressure fluid) and a low pressure port 704 connected to a second control fluid source (e.g., low pressure fluid).
  • An outlet port 706 is selectively connected to the high pressure port 702 or the low pressure port 704 by the configuration of a plunger 708 that moves in response to the controlled energizing and de-energizing of an electromagnetic coil 709.
  • the LRU 720 is configured to selectively connect a fluid outlet 722 to a selected one of the outlet port 706 or a fluid reference pressure source 740.
  • the fluid reference pressure source 740 can be the second fluid reference pressure source 640.
  • the LRU 720 is shown in an unlocked configuration.
  • the LRU 720 provides a fluidic circuit between the outlet port 706 and a fluid chamber 752 of the fluid linear actuator 750.
  • the fluid chamber 752 is separated from a fluid chamber 754 by a piston 756.
  • the piston 756 is urged to extend and retract due to a difference in the pressure of fluid in the fluid chamber 752 and the pressure of fluid in the fluid chamber 754.
  • the LRU 720 is shown in a locked configuration.
  • the LRU 720 provides a fluidic circuit between the fluid reference pressure source 740 and the fluid chamber 752 of the fluid linear actuator 750.
  • the piston 756 is urged to extend and retract due to a difference in the pressure of the fluid reference pressure source 740 and the pressure of fluid in the fluid chamber 754.
  • the fluid reference pressure source 740 is at a pressure that is greater than that of the fluid in the fluid chamber 754, thereby urging extension of the fluid linear actuator 750 and reversibly locking the actuator 750 in the extended configuration.
  • the fluid reference pressure source 740 may be at a pressure that is less than that of the fluid in the fluid chamber 754, thereby urging retraction of the fluid linear actuator 750 and reversibly locking the actuator 750 in the retracted configuration.
  • the fluid linear actuator 750 can be substituted with a fluid rotary vane actuator, a fluid rotary piston actuator, a fluid motor, or any other appropriate fluid-actuated apparatus.
  • FIG. 8 is a flow diagram of an example process 800 for locking out a servo valve.
  • the process 800 may be performed using any of the servo valves 100, 200, 300, 400, and 610, or the systems 500, 600, and 700 of FIGs. 1A-7B.
  • a valve is provided.
  • the servo valve 100, 200, 300, 400, or 610, or the solenoid valve 710 can be provided.
  • a lockout assembly is provided.
  • the lockout assembly 150, 250, 380, or 480, or the LRU 620 or 720 can be provided.
  • the lockout assembly is actuated into a first configuration.
  • the rotary cam 156 is rotated such that the eccentricity of the rotary cam 156 causes the rotary cam 156 to extend from the axis 157 substantially toward the open end 138.
  • the moveable housing end 152 translates axially within the open end 138 away from the axis 157 and urges the piston 108 into a predetermined one of the first or the second directions.
  • the piston is fixed into a selected first position.
  • rotary cam 156 holds the piston 108 in a position in which a fluid circuit from one or both of the openings 132a-132b (e.g., the high pressure fluid pathway) connects to the corresponding opening 140a-140b.
  • the method 800 can include actuating the lockout assembly into the second configuration, and releasing, by the lockout assembly, the piston from being fixed in the selected position such that the lockout assembly does not interfere with reciprocal axial movement of the piston.
  • the rotary cam 156 is positioned such that the moveable housing end 152 does not interfere with the axial translative movement of the piston 108.
  • the method 800 can include contacting the piston with a stop.
  • the lockout assembly 480 includes the stop 484 which can be threaded into the bore 482 to contact the piston 308, and can be threaded out of the bore 482 to not interfere with the axial translative movement of the piston 308.
  • the process 800 can also include locking the lockout assembly into at least one of the first configuration and the second configuration, where the lockout assembly also includes a lock operable to prevent disengagement of the lockout assembly from at least one of the first configuration and the second configuration.
  • the fastener 162 can be passed through the lever arm 158 and into the receptacle 160a or 160b to secure the lockout assembly 150 in the first configuration or the second configuration.
  • the method 800 can include preventing the flow of pressurized fluid from the fluid chamber. In some implementations, the method 800 can include allowing the flow of pressurized fluid from the fluid chamber. For example, the lockout assembly 250 can be actuated to selectively allow or prevent fluid from flowing out of the first fluid pressure chamber 1 18.
  • the method 800 can include actuating the lockout assembly into the first configuration by threading the fastener through the threaded bore so as to contact the activation portion.
  • the stop 384 can be threaded into the bore 382 to contact flapper assembly 310 and can be threaded out of the bore 382 so as to not interfere with movement of the flapper assembly 310.
  • the method 800 can include fixing the fluid actuator into a selected fluid actuator position in response to fixing the piston into the selected position.
  • the second stage fluid actuator 510 can be urged into and kept in a selected actuation state, such as extended or retracted, or rotated clockwise or counterclockwise, in response to configuring the lockout assembly 150 in the locked configuration.
  • the method 800 can include providing a high-capacity fluid valve having a fluid control portion coupled to the actuator portion, and fixing, in response to fixing the actuator into the selected actuator position, the high-capacity fluid valve into a selected valve position.
  • the fluid actuator 550 can be coupled to the actuator portion 522.
  • the fluid actuator 510 is actuated in response to locking of the lockout apparatus 150, the fluid actuator 550 can be fixed into a predetermined position.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Driven Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
PCT/US2015/055294 2014-10-14 2015-10-13 Hydraulic actuator lockout WO2016061079A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580067731.0A CN107002718B (zh) 2014-10-14 2015-10-13 液压促动器锁定
EP15790724.7A EP3207262A1 (de) 2014-10-14 2015-10-13 Hydraulische aktuatorsperre

Applications Claiming Priority (2)

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US14/514,181 US9625053B2 (en) 2014-10-14 2014-10-14 Hydraulic actuator lockout
US14/514,181 2014-10-14

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WO2016061079A1 true WO2016061079A1 (en) 2016-04-21

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EP3587832B1 (de) * 2018-06-24 2024-04-03 Hamilton Sundstrand Corporation Servoventilgehäuse
JP7017498B2 (ja) * 2018-10-19 2022-02-08 株式会社鷺宮製作所 電磁弁
IT201900010731A1 (it) * 2019-07-02 2021-01-02 C Matic S P A Innesto rapido migliorato
WO2024130449A1 (en) * 2022-12-23 2024-06-27 Sanctuary Cognitive Systems Corporation Low-power hydraulic valve, and applications thereof in robot systems

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Also Published As

Publication number Publication date
EP3207262A1 (de) 2017-08-23
US9625053B2 (en) 2017-04-18
US20160102778A1 (en) 2016-04-14
CN107002718B (zh) 2019-05-28
CN107002718A (zh) 2017-08-01

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